Chassis lubrication



Nov. 13, 1934. I .J. BIJUR 1,980,780

CHASSIS LUBRICATION Filed Sept. 20, 1930 4 Sheets-Sheet l ATTORNEYS Nov.13, 1934. J. BIJUR 1,980,780

I CHASSg S LUBRICATION Filed Sept. 20, 1930 4 Sheets-Sheet 3 Nov. 13,1934.

J. BIJUR CHASSIS LUBRICATION Filed Sept. 20, 1939 i J l l 176 174 54% 4Sheets-Sheet 4 -J I VINVENTORQ use klh' 'ur I QBY p p dwmnwdw ATTORNEYfiPatented Nov. 13, 1934 UNITED STATES 1,9s0,'7s0- I CHASSIS LUBRICATIONJoseph Bijur, New York, N. Y., assignor to Auto Research Corporation, acorporation of Delaware Application September 20, 1930, Serial No.483,165

32 Claims.

The present invention, considered in its broader aspects, is concernedwith the automatic lubrication of machinery from a central source oflubricant, but finds its preferred embodiment in the field of chassislubrication. The following specification, therefore, while recognizingthe broader utility of the invention, will concern itself specificallywith the problem of chassis lubrication and the manner in which thepresent apparatus satisfies the requirements of this type of machine.The more or less universal adaptability of the system to other machines,or groups of machines, will become apparent as the description proceeds.

An object of the invention is to provide a system of this character inwhich the feed of oil to the system is wholly automatic occurringperiodically at cyclically intermittent intervals during normal runningof the vehicle without the exercise of care or attention on the part ofthe operator, and so designed that emission of oil is prevented whilethe vehicle is standing still.

Another object is to provide for the immediate application of the freshlubricant to the bearings whenever a car that has been long idle is setin motion, this auxiliary or emergency lubricant feed occurringindependently of the regular lubricant feed cycles.

Another object is to provide an efficient and automatic mechanism forcontrolling the periods of pump effectiveness.

Other objects will be in part obvious during the course of the followingspecification and will be in part pointed out therein.

In a preferred embodiment of the invention, the supply device embodies aforce pump by which successive small charges of lubricant from a centralreservoir are forced into the distributing conduit system, thussubjecting the distributing system to a rapidly succeeding series ofpressure impulses by which the lubricant is forced through therestricted outlets in proportions predetermined by proper calibration ofsuch outlets.

During normal operation of the vehicle, timing mechanism renders thepump at cyclically succeeding intervals alternately efiective andineffective to deliver lubricant to the system.

The pump, preferably of the plunger type, may be conveniently embodiedin a unitary structure at the bottom of the lubricant reservoir, and thetiming mechanism may also be conveniently housed in or intimatelyassociated with the reservoir.

Preferably, the pump plunger is of relatively small diameter and arelatively small operating impetus applied thereto is operative to causea material rise in pressure in the conduit system, which is at all timesfilled with substantially incompressible lubricant. Thus, regardless oflubricant viscosity, a more or less uniform volume of oil will enter thesystem at each effective reciprocation ofthe pump.

Among various sources of power for pump actuation, I have shown aplurality of modes of utilizing vibratory energy developed in vehicletravel. The vibratory impulses may be applied to the p mp from anassociated oscillating or swinging inertia member. a I

When the vehicle is running at a constant speed, the vibration-sensitiveinertia actuated member will tend to vibrate rapidly so that either thecapacity of the pump should be exceedingly minute, or the periods ofeffective pump operation short and infrequent. I

There are many ways in which the pump might be rendered ineffective atthe desired intervals, such, for instancaas the automatic mechanicaldisconnection of the pump from its power source, the automatic closingof the inlet or outlet valves of the pump, the by-passing of the pumpdischarge back to the reservoir, or the cutting off of the supply oflubricant at some point in the pump intake line. In the present case,the latter mode of procedure is preferred, especially in view of thefact that a gravity 'oil feed to the pump is used. Gravity flow is upthrough a freely vented filter chamber located below the pump level, andby overflow from this chamber to the pump. By cutting off the fiow fromthe reservoir to the filter chamber, the pump, after using up the smallquantity of oil which has overfiowed from the chamber, simply runs idlyuntil communica-' tion between reservoir and filter chamber is restored.t

The timing mechanism may be actuated by various means to periodicallyopen and close a flow valve between reservoir and filter chamber; Oneefiective' form of control is directly from the pump actuating means sothat the pump will be rendered inoperative after the plunger has beenreciprocated a predetermined number of times. The timing means mayconveniently include a valve operating reduction gear train operatedfrom the pump actuating mechanism by a step by step arrangement such asa ratchet and pawl.

The auxiliary or emergency priming means which assures immediate supplyof lubricant to the bearings of a car after it has long stood idlepreferably includes a priming chamber having an outlet into the pumpintake line, between the main supply valve and suction line, andarranged to accumulate oil by slow seepage from the reservoir. Thus,even though the main control valve be closed, the pump will have anauxiliary supply of lubricant available to meet the special requirementsof such emergency starting conditions.

The invention may be more fully understood from the followingdescription in connection with the accompanying drawings, wherein:

Fig. 1 is a perspective fragmentary view of an automobile, the chassisof which is lubricated in accordance with the invention.

Fig. 2 isa detail of one of the drip plugs ,of' the system.

Fig. 3 is a vertical sectional view through an automatic liquid supplyand feed apparatus constructed in accordance with the invention.

Fig. 4 is another vertical sectionalview therethrough takenapproximately on the line 4-4 of Fig. 3.

Fig. 5 is a sectional plan view staggered line of 5 -5 of Fig. 3.

' Fig. 6 is a view similar to Fig. 3 butillustrating a modification andtaken on line 66 of Fig. 7.

Fig. 7 is a sectional plan view on the line 7-7 of Fi 6.

Fig. 8 is an enlarged vertical sectional detail taken approximately online 88 of Fig. 7.

Fig. 9 is an elevational detail of the mechataken on the nism forcontrolling the operative and inoperaof conduits 13, preferably liquidfilled and nondilatable, which extend along various structural parts ofthe vehicle and deliver through drip plugs 14 to the various bearings.

The supply unit of the present invention may be embodied in a widevariety of lubricant systems, one form of which is shown in my priorpatents, No. 1,632,771, 1,732,212 and 1,746,139 which systems include aplurality of freely intercommunicating liquid filled distributingconduits,

' the outlets of which may be supplied with suitable metering devices.By way of example one of these metering devices, is illustratively shownupon Fig. 2. This device comprises a fitting 15 having a valve 16 with aseating facing 17 of varnished silk urged against and adapted to takethe imprint of the sharp seat 18. Coiled compression spring 19 reactingagainst a retaining cup 20 presses the valve against its'seat. Astrainer 22 of wool-felt, backed with wire mesh 23 is plugged into thesocket 21 at the opposite end of the fitting. Between the valve and thestrainer is the restriction pin 24, fitting in a correspondinglongitudinal bore. The flow resistance of the drip plug depends upon theprecise diameter of the pin or wire 24, the bore of all drip plugs beingof the same diameter, the rating of a plug being determined by selectionof a pin of the proper diameter. In practice, each drip plug has amarking (not shown) which indicates its rating.

At the inlet of each drip plug fitting is a steel bushing 25, preferablypress-fitted and retaining the strainer 22 in place. A threaded nut 26reacts at its inner end against a compression coupling sleeve 28. Thesleeve is wedged inwardly by the bushing against the feed pipe 21 (abranch or end of one of the conduits 13) which at its outlet end abutsthe shoulder 25' in the bushing 25.

Referring first with particularity to Figs. 3 to 5 inclusive, and 10 and11, there is illustrated a unitary assemblage consisting of thereservoir R, the pump P arranged in a base casting of the reservoir, anda motor, such for instance as the jiggle weight W, thelatter with itsassociated mechanism being preferably accommodated in a separate housing93 on top of the reservoir. Lubricant from the reservoir flowsgravitation ally into a filter chamber C formed in the base casting at alower level than the pump and upwardly through the filter F to the pump.The timing mechanism which periodically cuts off the flow of lubricantto the filter chamber and thereby causes the pump to run idly ispreferably mounted within the reservoir and indicated generally at T.

More specifically, the reservoir itself consists of a pair of generallycup-shaped members, the

upper inverted member 30 having a flanged mouth 31 receiving the mouthof the lower cup 32 and providing an overlap which may be welded. Member30 is preferably provided with an integral upstanding filling neck 33receiving a suitable vented closure cap 34.

The base casting, which in the present instance is disposedsubstantially below the bottom of the reservoir R. is reduced at itsupper end as at 35 to receive a downwardly turned flange 36 of the lowercup 32. This flange defines an opening in the cup bottom which is shapedin accordance with the shape of the casting and the casting and flangemay be conveniently welded or otherwise secured together inlubricant-tight relationship. I

The casting may assume many forms. In the present instance as best seenin Fig. 5, it is of general pear-shape in horizontal cross section, thelarger casting section 37 accommodating the filter chamber C and thesmaller casting section 38 accommodating the pump P.

The filter chamber is formed by a downwardly facing socket 39 in thebase casting into which is screwed a cup-like plug 40, seating against apacking ring 41 to prevent leakage of lubricant therearound and having awell or sediment trap 42 in its bottom. Filter F preferably comprises apad or mat of wool-felt, the edges of which are clamped against adownwardly facing shoulder 43 in socket 39 by a cylindrical clampingmember 44 resting on the bottom of the cup and urged into mat clampingpositionas the cup is screwed home. The felt pad may be convenientlybacked by a wire cloth screen 45, the edges of which are pressed by themat against a second and higher downwardly facing shoulder 46 in thesocket 39. Member 44 is of less diameter than the'socket and defineswith the socket wall an annular oil inlet space 44a from which the oilflows to the filter chamber proper through openings 53 in the member 44.

The means for controlling the gravitational flow of oil from thereservoir to the filter chamber includes a ball check valve 47 normallyurged upwardly by coiled expansion spring 48 against a downwardly facingseat 49. The spring is backed against an upwardly facing shoulder 50 ina vertical bore 51 of the casting, this borecommunicating with thefilter chamber through an inclined passageway 52, which empties into theannular space 44a.

The enlarged upper end 54 of the vertical passageway 51 receives thependant apron portion 55 of a valve casing 56, which provides theaforementioned Valve seat 49. Oil from the reservoir P355 55 170 thevalve through ports 57 in the casing 56. A pin 58 sliding in the casingacts when depressed to unseat the ball check 47. The high side of a cam59 rotated by the timing mecha-' nism, to be later described, isoperative to periodically depress the pin 58 and unseat the valve. 4

The force pump P (Fig. 10) which receives oil from the filter chamberand delivers itto the conduit system 13 is of high powerbut of minutecapacity. An upstanding post 60 integral with the base casting may bevertically bored to form the pump cylinder in which works the long metalpump 51 of a diameter which is approximately equal to or smaller thanthe diameter of the conduits 13 of the distributing system. The pumpchamber is cooperatively fornied'by the inner upper end of a downwardlyfacing socket 62 in the casting and the top of a plug member 63 screwedinto the socket. Preferably the flanged upper end 64 of the plug pressesa packing ring 65 against the inner end of the socket and a flange 66 atthe outer end of the plug presses a second packing ring 67 against thelower face of the casting. Block 63 is provided with a central verticalbore, the lower end 67 of which is enlarged and threaded to receive thenipple 68 on the fitting member 12. The upper end of this bore isreduced at 70 and its upper extremity is further reduced at 71. To theend of the plunger is attached a stem '73 which is adapted to crack openthe valve 72 when the piston is in its lowermost position. The valveitself is normally springseated against a downwardly facing seat 74 inthe bore '79 by the coil spring '75 backed against a cup member 75press-fitted into the bore. The cracking open of the valve at the bottomof the plunger stroke permitsthe air compressed on the downward strokeof the plunger to escape from the pump cylinder and lessen the period ofprimmg.

The inlet valve of the pump preferably cornprises an annulus '77 restingon an upwardly facing seat 78 and communicating through a plurality ofL-shaped passageways 79 with an annular groove 80 in the plug 655.Groove 80 receives oil from the top of the filter chamber through aninclined passageway 81. The annular inlet valve lifts automatically onthe up-stroke oi the pump plunger to an extent limited by stop pins 77a,and is seated by the pressure or" entrapped lubricant as the plungerstarts to descend.

It may be noted at this juncture that the use of such apparentlydelicate valving in connection with a high power, although smallcapacity pump, is rendered possible by the very effective filteringmeans which insures the-passage of absolutely clean oil to the pump andprevents any minute foreign particles from reaching and lodging underthe valves. The passageway 81 from the filter chamber to the pump isfreely vented by a pipe carried by a hollow plug 91 fitted into avertical passageway 92 at the top of the base casting and intersectingthe oil passage 81. The open top of the pipe 90 is preferably disposedabove the top of the reservoir and desirably located within the housing93 for the operating weight W. This housing is formed with a ventopening 94 and preferably comprises an inverted cup-shaped memberwelded, press-fitted or otherwise secured in telescoped relationshipwith a collar 95 on top of the reservoir.

In order to guide the vertical reciprocating movement of the weightactuated plunger operating rod 96, a hearing bushing 97 is secured in asuitable opening in the top of the reservoir. This bushing is of generalcup-shape with its hottom of substantial thickness to provide an adequate guide for the enlarged portion 98 of the rod. A collar 99 screwedinto the upper threaded end of the bushing end 97 is centrally aperturedat 100 for free passage to the pump rod and cooperates with-the bottomof the bushing 97 to limit the range ofvertical reciprocatory movementof the rod. This limiting action is attained by pinning a collar 101 tothe rod between the telescoped members 9? and 99 so that they serve asstops for the collar and limit the upward and downward movement of therod. The range of rod,

movement-is readily adjustable by screwing the 1 member 99 further intoor out of its associated bushing. At its lower end, rod 96 is suitablyconnected to the axially aligned plunger of the pump, as by ball andsocket joint 102.

At its upper end, within the housing 93, the rod carries a fixed disk103, grooved at 104 near its outer edge to provide a seat for a coiledexpansion spring 105, upon the upper end of which rests an outwardlyextending flange 106 of the inertia weight W, whereby the weight iscarried by the cushioning spring and its load transmitted through thedisk 103 to the rod 96 and the pump plunger 61. The weight is preferablymounted for vertical sliding movement on a sleeve 10? encircling the rod96 above the en largement 98. This sleeve at its lower end abuts ashoulder 98a defined by said enlargement. Hardened steel bushings 109arranged within enlargements of the central bore 110 of the weightinsure free sliding movement thereof on the sleeve 107. The sleeve 107is held in position by a nut 111 screwed on to the top of the rod 96 andthe movement of the weight in both directions is impositively limited byflat springs 112 and 113 arranged respectively at the top and bottom ofthe sleeve. In order to insure the desired cushioned impact against thefiat stop springs, the upper and lower faces of the gen erallycylindrical weight are provided with circular recesses 114 so that theweight will strike only the ends of the springs.

On the upward movement of the weight, it will strike spring 112 and actthrough the nut 111 to lift the rod 96 and elevate the pump plunger 61to an extent limited by the collar 99. As the Weight gravitationallyfalls back, the load thereof is transmitted through the coil spring 105to the pump rod so that the pump has a sharp, quick intake or suctionstroke and a relatively slow but positive expelling stroke.

In normal operation of the vehicle the spring cushioned weight W maygradually develop a more or less periodic vertical sway or vibration, thamplitude of which will be considerably in excess of the range of themovement of the pump rod and the pump will be actuated in asubstantially uniform manner by the jiggle weight. Violent vibrations,while productive of a wider range of movement of the weight, areinoperative to vary the effective stroke of the plunger.

Similarly the violence of such vibrations is inoperative to varysubstantially the uniform speed of the reduction gear which acts torotate the cam step by step and thereby intermittently miseat the valve47. This reduction gear mechanisrn preferably includes a ratchetwheelfixed on a horizontal shaft 121 mounted in journal bearings 122. Thesebearings may be formed by the circularly bent upper ends ofverticalbrackets or straps 123, welded, screwed or otherwise secured at124 to the base frame. The

ratchet wheel acts through a suitable intermedif ate gearing to rotatethe cam 59' or rather the counter shaft 125 which carries the cam. Thisgearing, in the present instance, is illustratively shown as comprisinga worm 126 on the shaft meshing with a wheel 127 on the counter shaft125. 1

The mechanism for imparting a step by step rotation to the ratchet wheel120 includes a pawl 128 fixed upon one end of ,a horizontal lever 129,the opposite end of which is pivoted at 130 to a bracket 131 secured tothe inner face of the reservoir wall. Preferably, the lever consists ofa pair of metal straps secured in side by side relationship andintermediate their ends fiared'outwardly in opposite directions tocooperatively define asleeve 132 through which thepump rod 96 works. Toimpart motion to the lever 129 from the reciprocating pump rod, a socketmember 133 is preferably inserted in the upper end of the sleeve 132. Areactance collar 134 resting against a pin 135 in the pump rod backs acoiled expansion spring 136 encircling the pump rodand acting on thesocket 133 to urge it against pin 137 on the pump rod. As the pump rodlifts on the impact stroke of the weight, it acts through the coilspring 136 to elevate the lever 129 and move the pawl 128 back one stepon the ratchet wheel. On the down stroke of the rod 96, pin 137 actsthrough the collar 133 to depress the lever 129 and causes the pawl 128to feed the ratchet wheel 120 forwardly one step. Inasmuch as the pawl128 is of the spring type and inasmuch as there is a certain amount offlexibility in the operating connections between the lever 129 and thepump rod, I may find it desirable to use an independent stop forlimiting the retraction or idle stroke of the pawl 128 and preventingany possibility of over-retraction. This stop, for the purposes ofillustration, has been shown as a screw 138 adjustably mounted andbacked in the top of the reservoir R by nuts 139 engaging the inner andouter voir top.

Preferably .a conventional associated with the ratchet wheel to hold thelatter against retrograde movement. This detent may be carried on an Lshaped bracket 141 held in place by the screws 124. The pawl is urgedinto detaining position against the ratchet wheel by a torsional spring142.

The operation of the self-timing supply and feed unit, described above,is substantially as follows:

Assume that the cam 59 is in the position of Fig. 4 so that the ballcheck 47 is shut. Assume also that the car is not in motion and that thefilter chamber is substantially full of oil. When the car is started andoperated in the usual manner, the jiggle weight W will immediatelybecome active in the manner described above to reciprocate the pumpplunger and to impart a detent pawl 140 is step by step feed movement tothe ratchet wheel 120 of the reduction gear train. Inasmuch as the pumpis free to suck air through the pipe 90, its reciprocation will beentirely idle and it will simply compress and then relieve pressure onthe air entrapped in the pump chamber.

' Since the piston 61 is unpacked, the air, when compressed, may leakwith substantial freedom therearound. Some of the air sucked in throughthe pipe will thus find its way into the reservoir and bubbling upthrough the oil will escape through the usual vent opening in theclosure cap 34.

The continued step by step rotation of the faces respectively of thereserratchet wheel will gradually shift the position of the cam 59 untilthe cam depresses the pin 58 and opens the valve 47. When this occurs,the gradual seepage of oil through the filter disk F will fill thepassageway 81 with oil and the filter disk F will fill the passage 81with oil and the oil will rise in the pipe 90 seeking its :own level. Assoon as the pump begins to receive oil, it will becomeactive to force acharge of oil into the piping system on each expelling stroke. Thepressure exerted against the incompressible body of oil in the system bythe small but powerful pump piston will be sufiicient to force throughthe restricted outlets of such system a total quantity of oil equal tothe increment which is supplied by the pump. In practice the periodicityof the weight vibrations and the correspondingly rapid action of thepump will result in application of a rapidly succeeding series ofpressure impulses on the liquid which is confined in the systern, theseimpulses following each other in such rapid succession and with suchuniformity that the fiow from the restricted outlets of the system issubstantially equivalent to a continuous and uniform flow while the pumpis pumping oil.

By the time the high side of the cam 59 has moved oif pin 58 and theball check 47 snaps to closed position, there may be a standing columnof oil in the pipe 90. Whether or not such a column is present will bedetermined by the relative rates of oil seepage through the filter andthe rapidity and capacity of the pump. Assuming such a column to bepresent, it will be used up by the pump even with the check 47 shut.after which the pump will again run idly until the cam goes around andagain depresses the check valve 47. It will be noted that the system isone which prevents gravitational drainage of lubricant through'therestricted outlets or drip plugs at times when the pump is operatingidly. This is due to the fact that the pump outlet valve is neverunseated except when increments of oil are being forced into the systemby the pump, and since the drip plug valves are normally sea"- ed therewill be no vent for the distributing system and no open outlet throughwhich a drip could occur even though one of the drip plug valves werenot fully closed.

In Figs. 6 to 9 inclusive, and Fig. 12, I have illustrated a modifiedform of construction which, while embodying certain of the principlesshown in Figs. 3 to 5 has certain inherent advantages over theconstruction just described.

One essential difference is the fact that I use a pump of largercapacity and runit at much more infrequent intervals. I'provide aninitial priming charge of oil so that oil will be supplied to thebearings whenever a car which has been standing idle for sometime is setin motion.

starting a car and running for some distance before oiling the bearings,even though the car has been stopped or stored during a normally idleperiod of the automatic feed pump. This form of invention is alsosuggestive of another manner in which vibratory energy may besuccessfully utilized for pump operation, the operating means in thisinstance comprising one of the spring shackles of the car, directlyconnected to the pump.

Here the reservoir R and its filling cap 34 are retained, but the basecasting 150 is generally.

circular in formation and instead of being disposed without the tank andbelow it, is arranged for the most part within the tank proper and abovethe level of the tank bottom. Only the sediment trapping well 151 of thefilter chamber 152 is disposed below the bottom of the reservoir. Thefilter chamber is substantially similar to that described above with oneor two minor exceptions. The wire screen 153, which backs the filter padF, instead of being pressed against a shoulder is provided withcorrugations 154 and is pressed against the top wall of the chamber.Also the filter clamping collar 155 is in this case a part of the plugwhich forms the bottom of the chamber and the main inlet port 156 fromthe reservoir which'communicates with the annular space 157 around thecollar is a horizontal port controlled by a rotary disk valve 158. Thefilter chamber instead of venting through the passage which leads to thepump communicates by a transverse passageway 159 with a priming chamber160, the latter having a vent pipe 161 at its top, terminating above theliquid level of the reservoir and supported at its upper end by aseparate plate or bracket 162 projecting into the neck of the fillingopening.

The priming chamber 160 is formed by a downwardly facing socket in thebase casting closed at its bottom by a block 163. Very slow seepage ofoil into the priming chamber from the reservoir may occur through thehighly restricted passageway 164 in the chamber wall.

Due to the fact that the vent pipe 161 is disposed directly under thefilling opening of the reservoir, this pipe and the priming chamberwill, under ordinary conditions, become partially filled with oilthrough the top of the pipe when- .ever the reservoir chamber isrecharged. The

importance of this is that recharging may often occur only after the oilsupply has been completely exhausted and during a period when the diskvalve 158 is closed. In such a contingency,

the oil will flow into the priming chamber through the passageway 157and will immediately supply the pump with much needed lubricant for thedistributing system, regardless of the position of the valve 158.

As suggested above, the pump, in this case, is of larger capacity, theunpacked plunger 165 working freely in a cylindrical bore 166 in anupstanding projection of the casting. The diameter of the plunger andbore, may, if desired, be somewhat larger than the diameter of thelubricant filled conduits of the system which is to be supplied, so thatlarger increments of oilwill be forced into the system at each expellingstroke of the pump. I

The fitting 167 through which oil flows to the various branches of thedistributing system is screwed into the threaded bottom of a verticalbore 168 axially aligned with the pump plunger. A sleeve 169 screwedinto this bore in advance of fitting 167 provides a downwardly facingseat 170 for the pump outlet valve 171, the latter being normally heldseated by coiled expansion spring 172.

The pump inlet valve may be conveniently mounted in the short verticalpassageway 173 which connects the filter chamber with the hori-. zontalinlet passage 174 of the pump. In assembling the inlet valve, a collar175 is forced upwardly against a downwardly facing shoulder 176 of thepassageway 173 by a hollow plug 177 screwed into the passageway from thebottom. This plug is recessed to accommodate and provide a seat for theinlet valve 178 which is thus free to float between this seat and thecollar 175'. The inlet valve is lifted on the up-strbke of the plunger165 and pressure seated on the expelling stroke thereof. 7

The reduction gear train and the mechanism for operating it are quitesimilar to those described in connection with Fig. 3. A lever 180 hasone end pivoted as at 181 on a bracket 182 fixed within the reservoir.lever carries a driving pawl 183 co acting with a ratchet wheel 184carried by shaft 185 journalled in the upper ends of brackets 186 fixedto the base casting. The detentpawl 187 for the ratchet is pivotallymounted at 188 between ears 189 projecting fromthe post or cylinder 166'and the spring for urging this detent against the ratchet is shown at190. The worm 191 on shaft 185 drives a gear which in the presentinstance serves as the rotary disk valve 158. This gear turns on thestub shaft 192 fixed to one of the brackets 186 and is spring pressedagainst the machined outer face 193 of the port 156 by a spring 194.

The plunger operating rod 195 is journalled in a suitable bearing sleeve196 pressed out of a plate 197 secured over an opening 198 in thereservoir top, and a petticoat 199 on the rod 195 protects the bearingopening for the rod 195 from rain and dust.

The operative connections between the lever 180 and the pump rod areidentical with those shown in Fig. 3 including the reactance disc 200backing the spring 201 which acts through the collar 202 to lift thelever as the pump rod rises. As the pump rod falls, the pin 203 workingagainst the collar 202moves the lever downwardly. The means fortranslating vibratory energy into reciprocation of the pump rod issubstantially identical with one of the means disclosed in my co-pendingapplication Serial No. 296,975, filed August 2, 1928. V

The rod has a collar 204 pinned thereto at 205 and a coiled expansionspring 206 encircling the rcd'and backed against the plate 197 actsthrough the collar to urge the rod downwardly and the pump piston todischarged position. A coiled contractile spring 207 anchored to one ofthe usual spring shackles 2080f the vehicle serves to transmit throughsuitable mechanism the vibration of the vehicle spring.

The intermediate mechanism includes a lever 209, one end of which isanchored through a suitablestud screw 210 and lock nuts 211 to thespring 207. This lever at its other end isbifurcated to straddle arocking transmission plate 212, and the bifurcated extremity of thelever fulcrums on cross-pin 213 mounted in ears 214 rising from theplate 197. A torsional spring 215 encircling the pin 213 is engaged withlever 209 and tends to hold the free end thereof in lifted position. Oneend of the rocking transmission plate 212 is located under theintermediate portion of the lever 209 for depression by a contact boss230 thereon. The other end of the transmission plate is apertured at 216for the reception of the upper end of the, pump rod, and nuts 217screwed on to the rod above the plate cause the plate to lift the rodagainst the action of spring 206 when the transmission plate is rockedin a clock-wise direction. The plate 212 also rocks about the pin 213 toan extent limited by nuts 218 and 219 on a screw 220 secured in thereservoir top as by a nut 221. Plate 212 has an opening-221 therein toreceive the screw 220. The operation of the pump in this case is asfollows:

The continual oscillation of the vehicle spring The free end of theIfilter pad to the pump inlet valve 1'78.

I ity flow for charging purposes.

i which includes a reservoir,

and acting intermittently to out while the car is in motion willperiodically draw down the lever 209 which by its pivotal-engagement canslide freely with respect to its transmission plate at thecontactboss'230. As the lever is depressed the transmission plate rocksabout the pin 213 until it is arrested by the nut 219, this rockingmovement of the plate serving to elevate the plunger rod 195 and therebyto complete the suction stroke of the-pump plunger. During the flexingreturn of the vehicle spring, torsional spring 215 restores the lever209 to its illustrated position and the spring 206 is released todischarge the force-pump, an'das an incident of such discharge swingthetransmission plate back to position of Fig. 6. With this form of theinvention the stop which limits the retraction of pawl 183 mayconveniently comprise an extension 240 of the screw 220.

The operation of this form of self-timing intermittent feeding device issubstantially as follows:

With the reservoir full of oil and with the disc valve 158 open, oilwill flow gravitationally into the filter chamber 152 and up through theThe charging or intake stroke of the pump exerts a substantial suctionin the filter chamber sufii cient to assist materially in drawing oilthrough the filter pad and not relying on seepage or grav- On thedischarge stroke, ,oil is forced past the outlet valve 171 and into thesystem. Periodically, and in fact during a large part of the time, thedisc valve 158 will be closed and the pump will be operating idly sinceit will have no liquid supply to handle.

In general principles, therefore, the operation is quite similar to thatof the supply and force pump unit of Fig. l, in that the pump issupplied with liquid at intermittent intervals and runs 1 idly atintermittentintervals.

The utility of the priming chamber 160, insofar as such utility relatesto a quick supply of-oil' for the pump when thetank is refilled hasalready been set forth. Another and more important i function of thispriming tank, however, is to insure an immediate supply of oil to thepump when the car has been standing idly for some time and regardless ofthe position of the valve 158. The very restricted seepage passage 164between the i priming chamber and the body of oil in the reservoir is sodesigned that a very slow seepage'of oil is continuously occurring andif the car stands idle for an appreciable length of time the primingchamber will gradually fill up with oil assur- 1 ing an immediately andpossibly a much needed shot of oil at the bearings as soon as the car isset in motion. 1 i I What I claim is: I

1. A central lubricating system of the character a force pump, aplurality of lubricant filled distributing conduits into which lubricantfrom the reservoir is forced by the pump, flow-retarding means at theconduit outlets, and timer means synchronized with the pump off thesupply of lubricant thereto from the reservoir.

2. In a continuously operating force pump, means for supplying liquidthereto, a valve in the supply line and means for automaticallyinterjmittently closing said valve,whereby said pump will be permittedto exhaust its lubricant supply and periodically will operate idly, saidmeans comprising a valve operating reduction gear train, and

means synchronized with the pump for imparting I a step by step motionto the reduction gear train.

prising a valve operating reduction gear train, I

and means synchronized with the pump for imparting a step by step motionto the reduction gear train, one gear of the train serving as a rotarydisc inlet valve forthe supply line.

4. As a new article of manufacture a liquid supply and feed unit for acentral lubricating system, said unit including a reservoir, a forcepump arranged in the lower portion or" the reservoir and means in thereservoir acting automatically to intermittently cut off the flow ofliquid from the reservoir to the pump, whereby said pump will bepermitted to exhaust its lubricant supply and periodically will operateidly.

5. As a new article of manufacture a liquid supply and feed unit for acentral lubricating system, said unit including a reservoir, a forcepump arranged in the lower portion of the reservoir, means in thereservoir acting automatically to intermittently cut off the fiow ofliquid from the reservoir to the pump, whereby said pump will bepermitted to exhaust its lubricant supply and periodically will operateidly, the supply passage mospheric pressure in said passage at a pointbe tween the valve and the pump inlet.

6. A supply and force feed unit for central lubricating systemsincludinga reservoir having a filling opening therein. a base castingconstituting part of the bottom of the reservoir and defining a pumpchamber and pump cylinder, a piston working in the cylinder and operatedby an energy source arranged exteriorly of the reservoir, a filterchamber in the base casting through which oil flows in its passage fromthe reservoir to the pump and having a flow retarding filter padtherein, a valve controlling the flow of oil from the reservoir into thefilter chamber and a vent to a point above the liquid level in thereservoir to maintain atmospheric pressure in said passage arranged inthe passage between the filter chamber and the pump chamber, wherebysaid pump will be permitted to exhaust its lubricant supply and willoperate idly, when the flow valve is closed.

7. A supply and force feed unit for central lubricating systemsincluding a reservoir having a filling opening therein, a base castingconstituting part of the bottom of the reservoir and defining apump-chamber and pump cylinder, a piston working in the cylinder andoperated by an energy source arranged exteriorly of the reservoir, afilter chamber in the base casting through which oil flows in itspassage from the. reservoir to the pump, a vented priming chambercommunicating with the filter chamber and means for permitting a slowseepage of oil into the priming chamber.

8. A supply and force feed unit for central lubricating systemsincluding a reservoir having a filling opening therein, a base castingconstituting part of the bottom of the reservoir and defining a pumpchamber and pump cylinder, a

iston working in the cylinder and operated by anenergy source arrangedexteriorly of the reservoir, a filter chamber in the base castingthrough which oil flows in its passage from the reservoir to the pump,apriming chamber, a vent com- 2 prising a vent pipe,'the inlet of whichis disposed at the filling opening of the reservoir whereby the primingchamber is filled through. the vent pipe as the reservoir is charged.

9. In a pump, a piston and a movable member for operating the piston, asupply line for the pump, a valve in the supply line, and a reductiongear train synchronized with the pump for periodically opening andclosing the valve.

10. In a pump, a piston and a movable member for operating the piston, asupply line for the pump, a valve in the supply line, a reduction geartrain for periodically opening and closing the valve, and means operatedfrom said movable member for actuating the reduction gear train.

11. In a pump, a piston and a movable member for operating the piston, asupply line for the pump, a valve in the supply line, a reduction geartrain for periodically opening and closing the valve, and means operatedfrom said movable member for actuating the reduction'gear train, saidmeans including a ratchet and pawl mechanism, the pawl of which iscontrolled by said movable member and which mechanism imparts a step bystep movement to the reduction gear train.

12. In a lubricating system of the character which includes a centralreservoir and a system of distributing piping, a continuously operatingpump for forcing lubricant into the distributing system and automaticmeans for regulating the lubricant feed to the pump and therebyintermittently causing the pump to run idly, said automatic meansincluding means to cause lubricant .to be admitted to the pump incharges, each charge being less than the amount of lubricant that thepump will discharge into the system between the periods of admission ofsaid charges.

13. In a lubricating system of the character which includes a centralreservoir and a system of distributing piping, a continuously operatingpump for forcing lubricant into the distributing system and automaticmeans for intermittently causing the pump to run idly, said automaticmeans comprising a valve controlling the flow of lubricant from thereservoir to the pump and a valve-operating reduction gear synchronizedwith the movement of the pump.

14. In a lubricating system of the class which includes liquid filledconduits and a central reservoir, a pump for introducing in rapidsuccession minute charges of lubricant into the conduit system and meansfor periodically causing the pump to run idly.

15. In a lubricating system of the class which includes liquid filledconduits and a central reservoir, a pump for introducing in rapidsuccession minute charges of lubricant into the conduit system and meansfor intermittently rendering the pump inoperative to feed lubricant.

16. In a lubricating system of the type which includes a plurality ofbranched distributing conduits, a central reservoir and pump unit of theclass described comprising a normal flow passage from the reservoir tothe pump and a valve controlling said passage, a priming chamber havingrestricted communication with the reservoir and adapted to be filled byslow seepage, said priming chamber communicating with said flow passagebetween the valve and the pump.

1'7. In a lubricating system of the type which includes a plurality ofbranched distributing conduits, a central reservoir and pump unit of theclass described comprising a normal fiow passage from the reservoir tothe pump and a valve controlling said passage, a priming chamber havingrestricted communication with the reservoir and adapted to be filled byslow seepage, said priming chamber communicating with said flow passagebetween the valve and the pump, and being freely vented.

18. In a lubricating system of the type which includes a plurality ofbranched distribut- 19. A lubricating system of the type which in-.

cludesa plurality of branched distributing conduits, a centrallubricatingsystem of the type which includes a plurality of brancheddistributing conduits, a central supply and metering unit comprising-aninertia weight, a rod adapted to be actuated by said inertia weight andforming a longitudinal bearing therefor and spring disks rigidlypositioned on said rod on either side of said weight and adapted toresiliently transfer motion from said weight to said rod, the spacingbetween. said disks being greater than the length of said weight.

20. In a lubricating system of the type which includes a plurality ofbranched distributing conduits, a central lubricating system of the typewhich includes a plurality of branched distributing conduits, a centralsupply and metering unit comprising an inertia weight, a casingenclosing the same, a connecting rod operatively connected to saidweight and passing through the bottom of said casing, a stop chamber inthe bottom of said casing and a stop upon said connecting rod adapted tobe positioned in said stop chamber, the motion of said rod beingrestricted by the contact of said stop against the top and bottomand aplurality of flow controlling outlets, a supply unit comprising areservoir and a pump, said pump including a central cylindricalpassageway,

- a piston enclosed in said passageway, a chamber axially aligned withsaid passageway and positioned therebeyond, an outlet valve in saidchamber, an annular chamber encircling said central passageway and anannular valve enclosed in said annular chamber.

22. In combination with a central lubricating installation including abranched distribution system and a plurality of flow controllingoutlets, a central supply unit comprising a pump having a body with acentral piston chamber, an axially aligned outlet valve chamber and anannular inlet valve chamber between said piston chamber and said outletvalve chamber, a piston in said piston chamber, a circular valve in saidoutlet chamber and an annular valve in said inlet chamber.

23. In a lubricating system, for a mechanism having a plurality ofspaced bearings to be lubri cated, a central lubricant reservoir, adistributing system discharging through a plurality of restrictedoutlets at the hearings to be lubricated, a pump having a capacity inexcess of the current needs of thebearings for force feeding lubricantfrom the reservoir into the system, means for continuously operatingsaid pump throughout operation of said mechanism actuated automaticallyby said mechanism and means automatiill-0 cally by said needs of thebearings cant from the reservoir into the system, means for continuouslyoperating said pump throughout operation of said mechanism actuatedautomatically by said mechanism, an intermediate receiver between saidreservoir and said pump.

receiving lubricant from said reservoir and feeding it to said pump, andmeans continuously driven from the mechanism for intermittentlysupplying lubricant thereto automatically actuated at predeterminedintervals in the operation of the mechanism. i

25. In a lubricating system for a mechanism having a plurality of spacedhearings to be lubricated, a central lubricant reservoir, a distributingsystem discharging through a plurality of restricted outlets at thebearings to be lubricated, a pump having a capacity in excess of thecurrent needs of the bearings for force feeding lubricant from thereservoir into the system, means for continuously operating said pumpthroughout operation of said mechanism actuated automatically by saidmechanism, a lubricant flow retarding means positioned between said pumpand said reservoir and means ahead of said flow retardin means toprevent flow of lubricant periodically from said reservoir to said pumpduring operation of said mechanism.

26. In a lubricant system for a mechanism '1 having a plurality ofspaced bearings to be lubricated, a central lubricant reservoir, 9.distributing system discharging through a plurality ofrestricted outletsat the bearings to be lubricated, a pump having a oapacityin excess ofthe current for force feeding lubricant from the reservoir into thesystem, means for continuously operating said pump throughout operationof said mechanism actuated automatically by said mechanism, and meansfor varying the discharge of said pump into said system by regulatingits supply during operation of said mechanism automatically driven bysaid mechanism.

27. In a lubricating system for a mechanism having a plurality of spacedbearings to be lubricated, a central lubricant reservoir, a distributingsystem discharging through a plurality of restricted outlets at thebearings to be lubricated, a pump having a capacity in excess of thecurrent needs of the continuously operating said pump throughoutoperation of said mechanism actuated automatimechanism, means formaintaining a supply of lubricant immediately accessible to said pump,and means continuously driven from the mechanism for feeding said supplyat intervals with quantities of lubricant from said reservoir which willnot sufiice to permit the pump to feed at full capacity during suchintervals.

28. In a lubricating system for a mechanism having a plurality of spacedbearings to be lubribearings for force feeding lubricantfrom thereservoir into the system, means for stricted outlets at the'bearings tobe lubricated, a pump having a capacity in excess of the current needsof the bearings for force feeding lubricant from the reservoir into thesystem, means for continuously operating said pump throughout operationof said mechanism actuated automatically by said mechanism, means formaintaining a supply of lubricant accessible to the pump, and constantand intermittent feed means. to permit lubricant to flow from saidreservoir to said supply.

29. In a lubricating system for a mechanism having a plurality of spacedbearings to be lubricated, a central lubricant reservoir, a distributingsystem discharging through a plurality of restricted outlets'at thebearings to be lubricated, a pump having a capacity in excess of thecurrent needs of the bearings for force feeding lubricant from thereservoir into the system, means 'for continuously operating said pumpthroughout operation of said mechanism actuated automatically by saidmechanism, an inlet chamber immediately accessible to said pump, saidchamber being provided with an air vent extending above the lubricantlevel of the reservoir so that said inlet chamber will always be open tothe atmosphere and atmospheric pressure will be maintained therein, anda plurality of flow passageways from said reservoir to said pump, one ofwhich is provided with a restriction and another of which is providedwith an intermittent actuated valve.

30. In a central lubricating installation for a mechanism having aplurality of spaced bearings, including a branched piping system leadingto said bearings and having metering outlets to said bearings, acontinuously operating pump actuated automatically only upon operationof said bearings and discharging its entire output into said system,said pump comprising means forsupplying liquid thereto, and means forintermittently cutting oh the liquid supply, whereby said pump will bepermitted to exhaust its lubricant supply and will operate idlyi v 31;In a central lubricating installation for a mechanism having a pluralityof spaced bearings, including a branched piping'system leading to saidbearings and having metering outlets to said bearings, a continuouslyoperating'force pump actuated automatically only upon operation of saidbearings and discharging its entire output into said system, said pumpcomprising means for supplying liquid thereto, a valve in the supplyline and means for automatically intermittently closing said valve,whereby said pump will be permitted to exhaust its lubricant supply andwill operate idly;

f 32. In a central lubricating installation for a mechanism having aplurality of spaced bearings, including a branched piping system leadingto said bearings and having metering outlets-to saidbearings, a forcepu'mp'actuated automatically only upon operation of saidbearings anddischarging its entire output into said system, said pump comprisingmeans for supplying lubricant thereto, a valve -in the supply line andmeans for "automatically intermittently closing said valve, whereby saidpump will be permitted to ex- I haust its lubricant 'supply and willoperate idly, said means comprising a valve operating reduction geartrain.

. l JOSEPH BIJUR.

